US10871184B2 - Journal bearing and rotary machine - Google Patents

Journal bearing and rotary machine Download PDF

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Publication number
US10871184B2
US10871184B2 US16/167,827 US201816167827A US10871184B2 US 10871184 B2 US10871184 B2 US 10871184B2 US 201816167827 A US201816167827 A US 201816167827A US 10871184 B2 US10871184 B2 US 10871184B2
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Prior art keywords
key member
pad
curved surface
bearing
central axis
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US16/167,827
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US20190128272A1 (en
Inventor
Takashi Oda
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Mitsubishi Heavy Industries Compressor Corp
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Mitsubishi Heavy Industries Compressor Corp
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Assigned to MITSUBISHI HEAVY INDUSTRIES COMPRESSOR CORPORATION reassignment MITSUBISHI HEAVY INDUSTRIES COMPRESSOR CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ODA, TAKASHI
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/12—Structural composition; Use of special materials or surface treatments, e.g. for rust-proofing
    • F16C33/122—Multilayer structures of sleeves, washers or liners
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/06—Multi-stage pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/02—Selection of particular materials
    • F04D29/023—Selection of particular materials especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/02—Selection of particular materials
    • F04D29/026—Selection of particular materials especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/047—Bearings hydrostatic; hydrodynamic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/057—Bearings hydrostatic; hydrodynamic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/03—Sliding-contact bearings for exclusively rotary movement for radial load only with tiltably-supported segments, e.g. Michell bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/26—Systems consisting of a plurality of sliding-contact bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/08—Attachment of brasses, bushes or linings to the bearing housing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2240/00—Components
    • F05B2240/50—Bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/50—Intrinsic material properties or characteristics
    • F05D2300/506—Hardness
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/44—Centrifugal pumps

Definitions

  • the present disclosure relates to a journal bearing and rotary machine.
  • a bearing device In rotary machines including rotating shafts of a centrifugal compressor, a steam turbine, a gas turbine, a pump, an engine, and so on, a bearing device is used to rotatably support the rotating shaft.
  • a bearing device there is a journal bearing having a bearing pad with a pad surface which is slidably in contact with a rotating shaft.
  • Patent Document 1 discloses a constitution in which a rotating shaft is rotatably supported by a plurality of bearing pads provided on an outer side of the rotating shaft in a radial direction.
  • each of the bearing pads has a pivot substantially at a center thereof.
  • the bearing pad can be swung by bring this pivot into contact with a support metal on an outer side in the radial direction.
  • the pivot has a spherical protrusion at a tip end thereof.
  • the bearing pad is in point contact with the support metal and can be swung in an axial direction and a circumferential direction of the rotating shaft by bringing the spherical protrusion into contact with the support metal.
  • Patent Document 1 Japanese Unexamined Patent Application, First Publication No. S63-303214
  • the present disclosure provides a journal bearing and a rotary machine in which reliability of the journal bearing can be improved by minimizing damage to a bearing pad.
  • a first aspect of the present disclosure is a journal bearing including a plurality of bearing pads having pad surfaces configured to slidably come into contact with an outer circumferential surface of a rotating shaft and disposed at intervals in a circumferential direction around a central axis, a key member provided at a part of a pad rear surface which faces radially outward in the bearing pad, having a curved surface which is curved around an axis parallel to the central axis, configured to extend to have the same cross-sectional shape in a direction of the central axis in which the central axis extends, and formed of a material having a hardness higher than that of a material forming the pad rear surface of the bearing pad, and a housing having a support surface in contact with a part of the curved surface of the key member in the circumferential direction and configured to support the key member and the bearing pad to be swingable from an outer side in a radial direction of the key member and the bearing pad.
  • the curved surface of the key member extends to have the same cross sectional shape in a direction of the central axis of the rotating shaft, the curved surface is in line contact with the support surface of the housing in a direction parallel to the central axis. Therefore, wear of the curved surface of the key member can be minimized as compared with a case in which it is in point contact with the support surface of the housing. Further, since the hardness of the key member is higher than that of the pad rear surface, the wear of the curved surface can be further minimized.
  • the bearing pad may have a key member mounting surface orthogonal to the radial direction
  • the key member may have a fixed surface which faces the key member mounting surface and is orthogonal to the radial direction.
  • the fixed surface of the key member is in surface contact with the key member mounting surface of the bearing pad. Therefore, the wear of the bearing pad can be minimized at a contact portion between the key member and the bearing pad.
  • journal bearing of a third aspect of the present disclosure in the first or second aspect, only the curved surface may be in contact with the support surface of the housing when the key member and the bearing pad swing.
  • the journal bearing may further include a concave portion formed in the curved surface of the key member and recessed radially inward at an intermediate position of the curved surface in the circumferential direction, and a positioning member configured to protrude radially inward from the support surface and fixed to the key member in a state in which it is inserted into the concave portion.
  • the positioning member is inserted into the concave portion, and the movement of the key member in the circumferential direction can be restricted. Further, even when the positioning member is provided, the key member may bring the curved surface into line contact with the support surface of the housing in a portion other than the concave portion. Accordingly, it is possible to effectively minimize wear of the curved surface of the key member.
  • the curved surface of the key member and the pad rear surface of the bearing pad may have the same curvature radius in the circumferential direction.
  • the curved surface of the key member may have a smaller curvature radius in the circumferential direction than the pad rear surface of the bearing pad.
  • a region of the curved surface of the key member which is in line contact with the support surface of the housing becomes narrower in the circumferential direction. Therefore, resistance when the bearing pad swings is further reduced, and a following property of the bearing pad can be enhanced.
  • the region in which the curved surface of the key member is in line contact with the support surface of the housing becomes narrower, the pressure generated between the curved surface of the key member and the support surface of the housing increases.
  • the curved surface of the key member is formed of a material having high hardness, the wear of the curved surface can be minimized even in such a case.
  • a seventh aspect of the present disclosure is a rotary machine including a rotating shaft, and a journal bearing according to any one of the first to sixth aspects which supports the rotating shaft.
  • FIG. 1 is a schematic diagram showing a constitution of a centrifugal compressor according to an embodiment of the present disclosure.
  • FIG. 2 is a cross-sectional view orthogonal to a central axis of a journal bearing provided in the centrifugal compressor of the embodiment.
  • FIG. 3 is a cross-sectional view in a direction along the central axis of the journal bearing.
  • FIG. 4 is a cross-sectional view showing a constitution of a bearing pad of the journal bearing.
  • FIG. 5 is a view of a key member provided on the bearing pad when seen from an outer side in a radial direction.
  • FIG. 6 is a cross-sectional view orthogonal to the central axis of the journal bearing at a position in a direction of the central axial in which a positioning member is provided on the bearing pad.
  • FIG. 7 is a cross-sectional view showing a constitution of a bearing pad in a modified example of the embodiment of the journal bearing.
  • FIG. 8 is a schematic cross-sectional view of the bearing pad of the journal bearing taken along line VIII-VIII in FIG. 5 .
  • FIG. 9 is a schematic cross-sectional view of the bearing pad of the journal bearing taken along line IX-IX in FIG. 5 .
  • FIG. 1 is a schematic diagram showing a constitution of a centrifugal compressor according to an embodiment of the present disclosure.
  • a centrifugal compressor (rotary machine) 10 which is a rotary machine of the embodiment mainly includes a casing 3 , a rotating shaft 1 supported to be rotatable around a central axis O in the casing 3 , and an impeller 4 which is installed on the rotating shaft 1 and compresses a process gas (working fluid) G using a centrifugal force.
  • the casing 3 is formed in a cylindrical shape extending along the central axis O. An internal space of which a diameter is repeatedly contracted and expanded is provided in the casing 3 .
  • the casing 3 is provided to surround the impeller 4 by accommodating a plurality of impellers 4 in the internal space.
  • a flow path 2 which allows the process gas G flowing through the impeller 4 to flow from an upstream side to a downstream side is formed at a position between the impellers 4 .
  • a suction port 7 which allows the process gas G to flow into the flow path 2 from an outer side is provided on a first side of the casing 3 in a direction of the central axis O (direction in which the central axis O extends). Further, a discharge port 8 which is continuous with the flow path 2 and allows the process gas G to flow out to the outer side is provided on a second side of the casing 3 in the direction of the central axis O.
  • the rotating shaft 1 is supported by both ends of the casing 3 in the direction of the central axis O to be rotatable around the central axis O via a journal bearing 5 .
  • the rotating shaft 1 is supported on the first side in the direction of the central axis O to be rotatable in the direction of the central axis O via a thrust bearing 6 .
  • the impeller 4 is supported by the rotating shaft 1 to be rotatable around the central axis O.
  • the plurality of impellers 4 are provided at intervals in the direction of the central axis O of the rotating shaft 1 .
  • FIG. 1 shows an example in which six impellers 4 are provided, it is sufficient if at least one impeller 4 is provided.
  • Each of the impellers 4 compresses the process gas G suctioned from the first side in the direction of the central axis O and discharges it to an outer side of the central axis O in a radial direction.
  • the flow path 2 guides the process gas G discharged from the upstream impeller 4 located on the first side in the direction of the central axis O to the downstream impeller 4 located on the second side in the direction of the central axis O.
  • the process gas G is introduced from the suction port 7 into the flow path 2 .
  • the process gas G is compressed in each of the impellers 4 rotating around the central axis O together with the rotating shaft 1 and is discharged radially outward from an inner side in the radial direction.
  • the process gas G is compressed by passing through the impeller 4 and the flow path 2 provided in a plurality of stages within the casing 3 and then delivered from the discharge port 8 .
  • FIG. 2 is a cross-sectional view orthogonal to the central axis of the journal bearing provided in the centrifugal compressor of the embodiment.
  • FIG. 3 is a cross-sectional view in a direction along the central axis of the journal bearing.
  • FIG. 4 is a cross-sectional view showing a constitution of a bearing pad of the journal bearing.
  • FIG. 5 is a view of a key member provided on the bearing pad when seen from an outer side in a radial direction.
  • FIG. 6 is a cross-sectional view orthogonal to the central axis of the journal bearing at a position in a direction of the central axis in which a positioning member is provided on the bearing pad.
  • the journal bearing 5 includes a bearing housing (housing) 51 , a bearing pad 52 , and a key member 53 .
  • the bearing housing 51 is formed in an annular shape and supports the key member 53 and the bearing pad 52 to be swingable from the outer side in the radial direction.
  • the bearing housing 51 has a pad receiving groove 54 which is recessed radially outward from an inner circumferential surface 51 a thereof and is continuous in a circumferential direction around the central axis O.
  • the pad receiving groove 54 has a support surface 54 f which is circumferentially continuous at a groove bottom portion on the outer side in the radial direction. Therefore, the support surface 54 f faces inward in the radial direction.
  • a wall portion 54 w which stands inward in the radial direction is formed on both sides of the support surface 54 f in the direction of the central axis O.
  • a protrusion 54 k protruding toward the inner side of the pad receiving groove 54 is formed on the inner side in the radial direction.
  • a plurality of bearing pads 52 are provided radially inward with respect to the support surface 54 f of the bearing housing 51 at intervals in the circumferential direction.
  • five bearing pads 52 are provided at regular intervals in the circumferential direction.
  • the bearing pads 52 are accommodated in the pad receiving groove 54 of the bearing housing 51 .
  • each of the bearing pads 52 has an arc shape in a cross section orthogonal to the central axis O of the rotating shaft 1 and also has a curved plate shape which is wide in the circumferential direction.
  • the bearing pad 52 includes a pad surface 52 f which faces inward in the radial direction and a pad rear surface 52 g which faces outward in the radial direction.
  • the pad surface 52 f is capable of slidably coming into contact with an outer circumferential surface if of the rotating shaft 1 .
  • the bearing pad 52 includes a metal portion 56 which forms the pad surface 52 f , and a support portion 57 which supports the metal portion 56 from the outer side of the metal portion 56 in the radial direction.
  • the metal portion 56 is formed of, for example, a tin-lead alloy (a so-called white metal).
  • the metal portion 56 is formed to have a predetermined film thickness on an inner circumferential surface of the support portion 57 .
  • the support portion 57 is formed of, for example, a copper alloy or the like.
  • An outer circumferential surface of the support portion 57 is the pad rear surface 52 g .
  • the metal portion 56 and the support portion 57 are integrally formed.
  • a receiving concave portion 55 recessed inward in the radial direction is formed at an intermediate position of the pad rear surface 52 g of the bearing pad 52 in the circumferential direction.
  • the receiving concave portion 55 has a key member mounting surface 55 h orthogonal to the radial direction.
  • the key member mounting surface 55 h is formed radially inward from the pad rear surface 52 g.
  • the key member 53 is provided on a part of the pad rear surface 52 g which faces radially outward in the bearing pad 52 .
  • the key member 53 has a curved surface 53 r which faces outward in the radial direction and a fixed surface 53 s which faces inward in the radial direction.
  • the curved surface 53 r is curved in a convex shape around an axis parallel to the central axis O of the rotating shaft 1 to protrude outward in the radial direction.
  • the curved surface 53 r is continuously formed with the same curvature radius in the direction of the central axis O of the rotating shaft 1 , as shown in FIGS. 8 and 9 . Therefore, the key member 53 extends to have the same cross-sectional shape in the direction of the central axis O of the rotating shaft 1 .
  • a curvature radius R 1 of the curved surface 53 r is smaller than a curvature radius R 0 of the support surface 54 f of the bearing housing 51 . Therefore, in the key member 53 , only a part of the curved surface 53 r in the circumferential direction is in contact with the support surface 54 f . Since the curved surface 53 r of the key member 53 is continuous in the same shape in the direction of the central axis O, it is in line contact with the support surface 54 f in a direction parallel to the central axis O. Further, in the embodiment, the curvature radius R 1 of the curved surface 53 r is the same as a curvature radius R 2 of the pad rear surface 52 g of the bearing pad 52 .
  • the fixed surface 53 s is a plane orthogonal to the radial direction of the rotating shaft 1 . A part of a thickness of the key member 53 in the radial direction is accommodated (fitted) into the receiving concave portion 55 .
  • the key member 53 brings the fixed surface 53 s into surface contact with the key member mounting surface 55 h in the receiving concave portion 55 .
  • the key member 53 is fixed to the pad rear surface 52 g of the bearing pad 52 by performing punching at a plurality of portions P on a boundary with the pad rear surface 52 g on a side surface.
  • Such a key member 53 is formed of a material forming the pad rear surface 52 g of the bearing pad 52 , that is, a material having higher hardness than that of a material forming the support portion 57 , for example, carbon steel such as S25C or the like.
  • each of the bearing pads 52 is swingable together with the key member 53 around an axis parallel to the central axis O of the rotating shaft 1 .
  • a concave portion 58 recessed radially inward from the curved surface 53 r is formed in a center portion of the key member 53 in the circumferential direction and the direction of the central axis O.
  • a positioning member 59 which restricts movement of the key member 53 and the bearing pad 52 in the circumferential direction is provided at a position of the bearing housing 51 which is opposite to the concave portion 58 in the radial direction.
  • the positioning member 59 of the embodiment includes a bolt main body 59 a having a male screw portion on an outer circumferential surface thereof, and a spherical portion 59 b formed at a tip end of the bolt main body 59 a .
  • the positioning member 59 is fixed to the bearing housing 51 by screwing the bolt main body 59 a into a bolt insertion hole 51 h passing through the bearing housing 51 in the radial direction.
  • the spherical portion 59 b of the tip end protrudes radially inward from the support surface 54 f .
  • the spherical portion 59 b is inserted into the concave portion 58 of the key member 53 .
  • a predetermined clearance which does not hinder the swing of the key member 53 and the bearing pad 52 is provided between the spherical portion 59 b and the concave portion 58 .
  • the movement of the bearing pad 52 in the direction of the central axis O is restricted by the wall portions 54 w located on both sides in the direction of the central axis O.
  • the bearing pad 52 has a convex portion 52 t which protrudes on both sides in the direction of the central axis O.
  • the convex portion 52 t is located at an outer side of the protrusion 54 k of the wall portion 54 w in the radial direction.
  • the movement of the bearing pad 52 beyond a certain dimension inward in the radial direction is restricted by the convex portion 52 t colliding with the protrusion 54 k of the wall portion 54 w.
  • a lubricating oil supply nozzle 70 which supplies lubricating oil between the rotating shaft 1 and the bearing pad 52 is provided between the bearing pads 52 adjacent to each other in the circumferential direction.
  • a temperature sensor 60 which detects temperature of an oil film of the lubricating oil formed between the rotating shaft 1 and the bearing pad 52 by detecting temperature of the metal portion 56 is provided on the journal bearing 5 .
  • a sensor insertion hole 52 h recessed inward in the radial direction is formed in the pad rear surface 52 g of the bearing pad 52 .
  • the temperature sensor 60 is inserted into the sensor insertion hole 52 h .
  • a sensor wiring 61 of the temperature sensor 60 is disposed to extend in the circumferential direction through a gap formed between an inner circumferential surface of the pad receiving groove 54 of the bearing housing 51 and the bearing pad 52 .
  • the sensor wiring 61 is led out to the outer side in the radial direction through a wiring hole 51 j formed at a predetermined position of the bearing housing 51 .
  • the sensor wiring 61 is connected to a controller (not shown) and outputs an electric signal corresponding to the detected temperature to a controller.
  • the key member 53 is provided on a part of the pad rear surface 52 g of the bearing pad 52 . Since the curved surface 53 r of the key member 53 extends to have the same cross-sectional shape in the direction of the central axis O of the rotating shaft 1 , the curved surface 53 r comes into line contact with the support surface 54 f of the bearing housing 51 in the direction parallel to the central axis O. Therefore, a contact area is increased and wear of the curved surface 53 r of the key member 53 can be minimized as compared with a case in which it is in point contact with the support surface 54 f of the bearing housing 51 by a pivot or the like.
  • the key member 53 is provided on only a part of the pad rear surface 52 g of the bearing pad 52 , it is possible to minimize an increase in cost. In addition, it is possible to enhance durability of the journal bearing 5 and to reduce the labor and expense of maintaining the centrifugal compressor 10 .
  • the key member 53 has the fixed surface 53 s opposite to the key member mounting surface 55 h and orthogonal to the radial direction of the rotating shaft 1 . Due to such a constitution, the fixed surface 53 s of the key member 53 comes into surface contact with the key member mounting surface 55 h of the bearing pad 52 . Therefore, it is possible to increase the contact area at a contact portion between the key member 53 and the bearing pad 52 and to minimize the wear of the bearing pad 52 .
  • the pad rear surface 52 g of the bearing pad 52 does not collide with the support surface 54 f of the bearing housing 51 when the bearing pad 52 swings. Therefore, it is possible to prevent the pad rear surface 52 g of the bearing pad 52 from coming into contact with the support surface 54 f of the bearing housing 51 and being worn, or to prevent the temperature thereof from being increased
  • the key member 53 is in line contact with the support surface 54 f of the bearing housing 51 at a portion other than the concave portion 58 of the curved surface 53 r . Therefore, it is possible to effectively minimize the wear of the curved surface 53 r of the key member 53 .
  • the curved surface 53 r of the key member 53 and the pad rear surface 52 g of the bearing pad 52 have the same curvature radius in the circumferential direction around the rotating shaft 1 . Due to such a constitution, it is possible to easily process the curved surface 53 r of the key member 53 and the pad rear surface 52 g of the bearing pad 52 .
  • the curvature radius R 1 of the curved surface 53 r is set equal to the curvature radius R 2 of the pad rear surface 52 g of the bearing pad 52 , but the present disclosure is not limited thereto.
  • a curvature radius R 3 of the curved surface 53 r of the key member 53 can be formed to be smaller than the curvature radius R 2 in the circumferential direction around the rotating shaft 1 of the pad rear surface 52 g of the bearing pad 52 .
  • a region of the curved surface 53 r of the key member 53 which is in line contact with the support surface 54 f of the bearing housing 51 becomes narrower in the circumferential direction. Therefore, resistance when the bearing pad 52 swings is further reduced, and following property of the bearing pad 52 can be enhanced.
  • the region in which the curved surface 53 r of the key member 53 is in line contact with the support surface 54 f of the bearing housing 51 becomes narrower, the pressure generated between the curved surface 53 r of the key member 53 and the support surface 54 f of the bearing housing 51 increases.
  • the curved surface 53 r of the key member 53 is formed of a material having high hardness, the wear of the curved surface 53 r can be minimized even in such a case.
  • the present disclosure is not limited to the centrifugal compressor and can also be applied to other rotary machines such as engines as long as the rotating shaft is supported by the journal bearing.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Sliding-Contact Bearings (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
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DE102016106005B4 (de) * 2016-04-01 2019-12-24 Zollern Bhw Gleitlager Gmbh & Co. Kg Kippsegmentlager
WO2021124557A1 (ja) * 2019-12-20 2021-06-24 三菱電機株式会社 圧縮機システム、圧縮機および冷凍サイクル装置
CN111442027A (zh) * 2020-04-28 2020-07-24 宜兴市环宇轴瓦制造有限公司 一种增速齿轮箱用可倾瓦支撑轴承
DE102021124856A1 (de) 2021-09-27 2023-03-30 Voith Patent Gmbh Kippsegmentradiallager und Wellenanordnung

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US3339990A (en) * 1964-07-13 1967-09-05 Worthington Corp Lubricated bearing shoe
US3610711A (en) * 1970-04-15 1971-10-05 Westinghouse Electric Corp Tilting pad bearing and seal
US4039228A (en) * 1976-05-07 1977-08-02 Delaval Turbine, Inc. Tilting pad bearing
JPS63303214A (ja) 1987-06-04 1988-12-09 Mitsubishi Heavy Ind Ltd 軸受
US6767133B2 (en) * 2000-02-05 2004-07-27 Delaware Capital Formation, Inc. Tilting pad bearing arrangement
JP2006118552A (ja) 2004-10-20 2006-05-11 Mitsubishi Heavy Ind Ltd 軸受装置

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JPS57145815U (ja) * 1981-03-11 1982-09-13
JPS59116625U (ja) * 1983-01-28 1984-08-07 株式会社東芝 テイルテイングパツド軸受
JPH08145052A (ja) * 1994-11-24 1996-06-04 Mitsubishi Heavy Ind Ltd 動圧軸受
JP4929223B2 (ja) * 2008-04-11 2012-05-09 三菱重工業株式会社 軸受装置及び回転機械
WO2012137509A1 (ja) * 2011-04-05 2012-10-11 株式会社 東芝 軸受装置、水力機械
JP6101101B2 (ja) * 2013-02-08 2017-03-22 三菱重工業株式会社 ジャーナル軸受装置、これを備えている回転機械、及び回転機械の振動減衰方法

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Publication number Priority date Publication date Assignee Title
US3022123A (en) * 1959-09-21 1962-02-20 Waukesha Bearings Corp Tilting pad journal bearings
US3339990A (en) * 1964-07-13 1967-09-05 Worthington Corp Lubricated bearing shoe
US3610711A (en) * 1970-04-15 1971-10-05 Westinghouse Electric Corp Tilting pad bearing and seal
US4039228A (en) * 1976-05-07 1977-08-02 Delaval Turbine, Inc. Tilting pad bearing
US4039228B1 (ja) * 1976-05-07 1988-03-29
JPS63303214A (ja) 1987-06-04 1988-12-09 Mitsubishi Heavy Ind Ltd 軸受
US6767133B2 (en) * 2000-02-05 2004-07-27 Delaware Capital Formation, Inc. Tilting pad bearing arrangement
JP2006118552A (ja) 2004-10-20 2006-05-11 Mitsubishi Heavy Ind Ltd 軸受装置

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US20190128272A1 (en) 2019-05-02
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